Preventing torque-caused impair of a sliding support mechanism

ABSTRACT

Rack-and-pinion sliding support mechanisms and mechanical elements thereof are disclosed. One or more shafts are coupled to pinions configured to engage with one or more racks and configured to be driven by one or more motors. The rack and pinion are configured to provide vertical and horizontal displacement to reduce premature component wear leading to poor gear mesh caused to by forces on the mechanism during use. Motor assembly in such support mechanism is modified—as compared to current industrial versions—to prevent the destruction of motor—assembly housing by torques generated by the one or more motors and transferred to the pinions, thereby reducing motor failures.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation-in-part of the U.S. patentapplication Ser. No. 16/666,184, filed on Oct. 28, 2019, which is inturn a continuation of the U.S. patent application Ser. No. 16/268,235,filed on Feb. 5, 2019 and now issued as U.S. Pat. No. 10,480,627. Thedisclosure of each above-identified application is incorporated hereinby reference.

RELATED ART

Motorized sliding support mechanisms are well-known and used to supportstructures the positions of which need to be changed under differentcircumstances. An example is a motorized drawer. A more demandingexample application is a “slide-out” module, commonly included in arecreational vehicle (RV) or motor home. RVs frequently include livingspaces, which can be expanded when the vehicle is parked, to provideadditional room. These “slide-outs” extend from the outer walls of thevehicle and are suspended over the ground. For convenience, and becauseslide-outs (or slide-out sections) can be extremely heavy, it is oftendesirable to equip them with a motorized mechanism or driver toautomatically extend and retract the slide-out as desired. Some of thesemotorized mechanisms use a set of rack and pinions connected to thesides of the slide-out section(s). Electric motors drive the pinions,which are typically mounted in an assembly (including the motor andresiding within a compartment within a side portion of the vehicle). Thepinions, in turn, engage with the rack and drive a given slide-outforward or backward relative to the pinions.

Conventional motor-driven sliding support mechanisms—such as thosecurrently used for RV slide-outs—have multiple structural andoperational deficiencies. For example, the rack and pinions are prone tobinding or degradation (e.g., abrasion and wear of teeth on the pinionsand the corresponding grooves in the rack), which reduces the ability ofthe motor to slide the supported structure with the available electricalpower. Some conventional mechanisms were observed to poorly gear meshwith the rack under common operating conditions. Additionally, someconventional mechanisms were proven to fail to solidly couple the motorto the shaft and other components, which led to severed motor wires whenthe mechanism experienced unexpected movements or forces. These andother problems may cause the motor to fail. Furthermore, the mechanismscoupling the motor to the pinions frequently make it difficult orimpossible to move the mechanism manually in the event of a motorfailure. In the example of an RV slide-out, these failures may occur inremote locations while also making it dangerous or impossible to drivethe RV to a repair facility.

SUMMARY OF THE INVENTION

Improved sliding support mechanisms disclosed herein address at leastseveral particular deficiencies of known motorized sliding supportmechanisms. First, embodiments disclosed herein use racks and pinionsconfigured to ensure proper meshing between the pinion teeth and rackgrooves, even when the mechanism experiences mechanical forces whichwill tend to move these components out of alignment. For instance, whenan RV slide-out is deployed, the racks may experience a downward forcedue to weight of the slide-out which is suspended beyond the walls ofthe RV. Similarly, if the slide-out has a non-uniform mass distribution,or the RV rests on an unleveled surface, the racks and pinions mayexperience lateral torques that will tend toward misalignment of thepinions with their corresponding racks.

Second, embodiments disclosed herein enable the motor(s) to remainsolidly coupled to the shaft and other components at all times duringoperation of the mechanism, dramatically reducing the opportunity fordamage to the motor(s) and any electrical connections due to stressesexperienced during unexpected movements.

Third, the disclosed embodiments ensure that failures of the motorassemblies used in the motorized sliding support mechanisms aresubstantially prevented.

In particular, embodiments provide a sliding support mechanism having amain axis, which mechanism includes a) a first rack and a first pinion,the first pinion coupled to the first rack, the first rack havinga-translational axis; b) a motor assembly having a drive motor and agearbox enclosed in a first housing unit, and a rotor portiondimensioned to be partially inserted in said first housing unit when themotor assembly is complete, the rotor portion containing a rotor bearinghousing and a rotor passing therethrough (here, the first housing unitincludes a structural extension that protrudes radially with respect tothe main axis and beyond a radial extent of the rotor portion, wherestructural extension disposed at an end of the first housing unit thatfaces the rotor portion); c) a shaft having a first end and a secondend, the shaft coupled to both the rotor and to the first pinion at thefirst end of the shaft; d) a bearing configured to receive the shaft andencircle the shaft at a point between the rotor and the second end ofthe shaft; e) an upper housing coupled to the first end of the shaft anddirectly mechanically attached to said structural extension; and f) alower pinion assembly coupled to the second end of the shaft, where thelower pinion assembly includes an aperture dimensioned to receive thesecond end of the shaft. The mechanism is configured such that, in afirst state of operation, a fastener is positioned in the aperture suchthat the shaft and rotor are engaged; and in a second state ofoperation, the fastener is withdrawn by at least a fixed distance fromthe aperture, thereby disengaging the first end of the shaft from therotor such that the first rack translates freely along the firsttranslational axis when a force is applied to the support mechanism in adirection parallel to the first translational axis.

Embodiments additionally provide a sliding support mechanism is arecreational vehicle, which includes multiple sliding support mechanismunits structured as stated above.

Embodiment further provide a motor assembly (for use in a slidingsupport mechanism). The motor assembly includes a drive motor enclosedin a motor housing; a set of gears housed in a gearbox housing that hasfirst and second ends, and is coupled to the drive motor (here, thegearbox housing is affixed to the motor housing at a first end and has acollar at a second end). The motor assembly additionally includes arotor assembly having a rotor bearing housing, a rotor bearing disposedtherein, and a rotor shaft passing through the rotor bearing and coupledto the set of gears. Here, the rotor bearing housing is removablyaffixed to the gearbox housing at least at an outer periphery thereof,and a radial extent of the collar with respect to the axis exceeds aradial extent of the bearing housing with respect to the axis.

BRIEF DESCRIPTION OF THE DRAWINGS

Advantages of embodiments of the present invention will be apparent fromthe following detailed description of the examples of embodimentsillustrated in the drawings, if which like elements and components arelabelled with like numerals, and of which:

FIG. 1A is a perspective view of an embodiment of the sliding supportmechanism configured according to an idea of the invention.

FIG. 1B is a cross-sectional perspective view showing further details ofthe embodiment of FIG. 1A.

FIG. 1C is a detailed perspective view of selected elements shown inFIGS. 1A and 1B.

FIG. 2 is a cross-sectional view of an alternate embodiment in twodifferent configurations.

FIG. 3 presents exploded perspective views of selected elements and/orcomponents of an embodiment of the sliding support mechanism shown inFIG. 1A and FIG. 2.

FIG. 4 is a cross-sectional view of another alternate embodiment.

FIG. 5 is perspective view of an example of application of thealternative embodiment.

FIGS. 6A, 6B, and 6C present different views of portions of a modifiedmotor assembly for use with the embodiment of FIGS. 1A, 3, 5. FIG. 6A:exploded perspective view of the modified motor assembly; FIG. 6B:partially-exploded perspective view of the modified motor assembly; FIG.6C: partially-exploded perspective view of the modified motor assemblywith a cut-out, showing the contents of the motor assembly housing.

FIG. 6D: a perspective view of the embodiment of the modified motorassembly of the invention in spatial cooperation with a pinion assemblyof the sliding support mechanism.

FIGS. 7A, 7B, and 7C present various views of portions of aconventionally-structured motor assembly forming a part of theembodiment of FIGS. 1A, 3A.

Generally, the sizes and relative scales of elements in Drawings may beset to be different from actual ones to appropriately facilitatesimplicity, clarity, and understanding of the Drawings. For the samereason, not all elements present in one Drawing may necessarily be shownin another.

DETAILED DESCRIPTION OF THE INVENTION

Aspects and elements of the invention are disclosed in the followingdescription and related drawings directed to specific embodiments of theinvention. Alternate embodiments may be devised without departing fromthe spirit or the scope of the invention. Additionally, well-knownelements of discussed embodiments of the invention will not be describedin detail or will be omitted so as not to obscure the relevant detailsof the invention. Further, to facilitate an understanding of thedescription, discussion of several terms used herein follows.

For ease of illustration, descriptions of embodiments herein make use ofdirectional terms such as ‘upper’, ‘lower’, ‘inner’, ‘outer’, ‘top’,‘bottom’, et al. It should be understood that these terms are not meantto limit the embodiments herein by required any preferred orientationand, rather, are used to make spatial relationships between variousparts more readily understood with reference to the orientation of thefigures. It should also be understood that substantially similarcomponents are at times identified using a single reference number forclarity. For instance, each pinion belonging to a pair of pinions may besimply referred to as a pinion. It should also be understood that thepresent application makes reference to slide-outs and other similarstructures as examples only, to aid in understanding features andadvantages of the invention, and not to limit the invention to thespecific implementations of the slide-out and related structures.

FIGS. 1A, 1B illustrate key features of an example of a sliding supportmechanism 100. Referring to FIG. 1A, the mechanism 100 includes a shaftassembly 110 and a rack assembly 140. As shown, the shaft assembly 110includes a motor gearbox assembly 102) interchangeably referred toherein as a motor assembly), a shaft 104, a pinion 106, an upper shafthousing 120, and a lower shaft housing 130.

The motor assembly 102 is operationally attached to the upper shafthousing 120 with a motor coupling 122. The shaft assembly 110 isconfigured to couple to a rack 142. The shaft assembly 110 includes atleast one pinion 106 (shown in detail in FIG. 1B), which is dimensionedto couple to the shaft 104 and to engage the rack assembly 140. Thelower shaft housing 130 includes at least a pair of rollers 132 (one ofwhich is shown in FIG. 1A). The upper and lower housings also includevarious wear surfaces and house at least one bearing (these elements,which are not shown in FIG. 1A, are described below with reference toFIG. 1B). For convenience, the upper shaft housing 120 and the lowershaft housing 130, taken together with the components they embrace orhouse or include, may be referred to as a pinion assembly 112.

The rack assembly 140 includes a rack 142 and a recess 144, in which therack 142 is secured. The recess has a top surface 146, which forms aroof of the recess 144. The recess 144 includes a floor structure 148,which also forms or is dimensioned as an inverted U-shaped channel. Therack assembly 144 is shown with various holes to allow the rack assemblyto be secured to an external object or structure (not shown) in order toenable this object or structure to be translated along the long axis ofthe rack 142.

When the shaft assembly 110 is coupled to the rack assembly 140, therollers 132 rest within the channel 148 of the rack assembly 140. Therollers 132 are configured to roll or move along the channel 148,thereby reducing friction and allowing the motor gearbox assembly 102 tomore efficiently drive or effectuate the linear motion of the rackassembly 140 relative to the shaft assembly 110. The rollers 132, actingtogether with the walls of the channel 148, also serve to keep the shaftassembly 110 (and particularly the pinion 106) in alignment with therack 142, thereby countering any reactive back-torque on the rack 142during operation of the motor assembly 102 as well as any externaltorques.

FIG. 1B is a hybrid cross-sectional perspective view with cutaways,illustrating certain features of the embodiment of FIG. 1A in greaterdetail. In particular, portions of the upper shaft housing 120 are notshown (removed from FIG. 1B) to provide a clear view of the pinion 106.As shown, the pinion 106 has a main body with teeth configured to engagewith the teeth of the rack 142 as well as a collar immediately above theteeth. In some embodiments, the shaft 104 may be disposed to passthrough a circular opening in the pinion 106. The shaft has a key (notpictured), which fits into a slot (not shown) in the pinion 106. Theshaft 104 is encircled by a bearing 126. In some embodiments, the shaft104 may be optionally encircled by additional bearings (such as bearing136, for example, indicated to reside within the lower shaft housing130).

FIG. 1B also more clearly shows one of the rollers 132, which is coupledto the lower shaft housing 130 in at least one embodiment. Also shownadjacent to the roller is a lower wear surface 134, which protrudes fromthe lower shaft housing 130. The lower wear surface 134 provides a stopagainst excessive vertical (in the coordinate system of FIG. 1B)displacement of the rack assembly 140 (and particularly rack 142)relative to the shaft assembly 110 (and particularly the pinion 106). Inpreferred embodiments, the wear surface 134 is either constructed from amaterial softer than that of the area of the channel 148 (which the wearsurface is designed to contact) and/or is coated with such softermaterial. In some embodiments, this softer, referred to material is alsojudiciously chosen to reduce friction between the wear surface and thechannel 148. Although depicted as a continuous portion of the lowershaft housing 130, the lower wear surface 134 may be configured as aseparate object that couples to the rest of the lower shaft housing 130.It should be appreciated that the features of the wear surface 134described above confer certain advantages, among which there aredirecting or redistributing a greater degree of operational wear to apart that is more easily accessed for service, and allowing an exhaustedwear surface to be replaced (or recoated), thereby greatly extending theoperational lifetime of the overall support mechanism.

FIG. 1B also shows an upper wear surface 124 on the upper shaft housing120. Similarly to the situation with the lower wear surface 134, thiswear surface 124 also serves as a mechanical stop against excessivevertical displacement of the rack assembly 140 relative to the shaftassembly 110. In preferred embodiments, the upper wear surface 124 isformed from a material chosen to reduce friction between the wearsurface 124 and the channel 148 and softer than that of the roof 146formed by the recess 144. Although depicted as a continuous portion ofthe upper shaft housing 120, the upper wear surface 124 may beconfigured as a separate object that couples to the rest of the uppershaft housing 120. It should be appreciated that the features of theupper wear surface 124 described above confer similar advantages tothose discussed above in connection to the lower wear surface 134.

Additional details concerning the rollers 132, the wear surfaces 124 and134, and the lower shaft housing 130 are visible in FIG. 1C thatpresents an isolated perspective view of the lower shaft housing 130. Inparticular, FIG. 1C clearly shows both rollers 132 positioned on eitherside of the lower wear surface 134, which extends or located at a levelabove the height of the rollers 132, ensuring that the rollers 132 donot contact the floor 148 of the rack assembly 140 during the operationof the system 100. The rollers 132 are pictured as conventional camfollowers, but other devices or configuration are also suitable in agiven embodiment.

Various embodiments comprise a shaft assembly 110 with a pair of pinions108 and a corresponding pair of rack assemblies 140, each having a rack142 and other elements described above. FIG. 2 shows one such embodiment200 (only the shaft assembly 110 is shown). Embodiment 200 is shown intwo different configurations, 200 a and 200 b. Together, theseconfigurations illustrate a key feature of preferred embodiments: theability to manually disengage the shaft 104 from the motor gearboxassembly 102 (not pictured in FIG. 2). For greater ease in understandingdifferences between the two configurations, only elements arrangeddifferently between configuration 200 a and 200 b are labeled forconfiguration 200 b. Although the components of shaft assembly 110 maybe provided as discrete parts of sub-assemblies, portions of theforegoing discussion will describe shaft assembly 110 in a fullyassembled state.

FIG. 2 illustrates an embodiment 200 (in which the shaft assembly 110includes an upper pinion assembly 220 and a lower pinion assembly 230)in two configurations: 200 a and 200 b. The configuration 200 a of theshaft assembly 110 is the initial configuration (as it may be during theassembly, when the shaft 104 is uncoupled from the motor coupling 122,but is retained within the shaft assembly 110). When the shaft assembly110 is in configuration 200 b, the shaft 104 coupled to the motor 102.Each pinion assembly is structurally similar to the pinion assembly 112discussed in reference to FIGS. 1A and 1B. Each of the pinion assemblies220, 230 includes a pinion 106 as well as an upper bearing 126 and alower pinion bearing 136 through which the shaft 104 passes. Thesecomponents are housed jointly within the upper shaft housing 120 and thelower shaft housing 130, which are coupled together. The shaft 104 iskeyed in two locations, having an upper key 204 a and a lower key 204 b.These two keys (204 a and 204 b) fit into a recess (not shown) in eachpinion 106, coupling the shaft 104 to each pinion 106 when the shaft 104rotates. Additional detail of the pinions 106 and keys (204 a, 204 b)are discussed below, and are visible in greater detail in FIG. 3A.

The keys 204 a and 204 b are each made shorter than the overall lengthof the pinion 106, thereby allowing the shaft 104 to translate up anddown along a direction parallel to the length of the shaft assembly 110.The shaft passes through a fastener 210 at the bottom of the shaftassembly 110. The fastener 210 both holds the shaft 104 in place andallows the vertical (in the coordinate system of FIG. 3A) position ofthe shaft 104 to be adjusted to engage the shaft 104 with the motorcoupling 122 or disengage it from the motor coupling 122, as describedbelow.

The shaft 104 is provided with two annular extensions 206 a and 206 a,one or more of which may be attached to the shaft after the shaft 104 ispassed through the fastener 210 and the bearings (124, 134) within thetwo upper shaft housing 120 and lower shaft housing 130. These annularextensions may be configured as known structures (such as split-rings orother suitable structures) and serve to widen the shaft 104 where theextensions are installed. In some embodiments, the shaft 104 may beprovided with a recesses dimensioned to receive the annular extensions.As shown, in FIG. 2, the annular extension 206 a is placed just abovethe point at which the shaft 104 begins to pass through the top side ofthe fastener 210. The second annular extension 204 b is placed at thepoint where the shaft 104 exits the bottom of the fastener 210.

It will be appreciated that, when the shaft assembly 110 is initially inconfiguration 200 a, the shaft 104 is uncoupled from the motor coupling122, but is retained within the shaft assembly 110 by at least annularextension 206 a pressing against the top of edge of the fastener 210. Ifand when the fastener 210 is inserted further into the aperture 208 inthe bottom of the shaft assembly 110, the fastener 210 pushes againstthe annular extension 206 a, thereby pushing the shaft 104 upwardstoward the motor coupling 122.

When the fastener 210 is fully inserted into the aperture 208, the topend 202 of the shaft 104 is driven into the motor coupling 122, therebycoupling the shaft 104 to the motor 102 (not shown in FIG. 2). Asdepicted, the top end 202 of the shaft 104 resembles a hex bolt and isconfigured to mate with a correspondingly-shaped opening in the motorcoupling 122. The fastener 210 may be a suitable structure such as a pinor bolt with a channel dimensioned to receive the shaft 104. In certainembodiments, the aperture 208 may be threaded and the fastener 210 maybe configured with complementary threads. In these and otherembodiments, the fastener 210 may be configured to have a hexagonal cap,thus enabling the fastener 210 to be inserted and withdrawn usingstandard tools such as a wrench or crank.

When the shaft assembly 110 is in configuration 200 b, with the fastener210 fully inserted into the aperture 208 and the shaft 104 coupled tothe motor gearbox assembly 102, the shaft 104 may be disengaged from themotor gearbox assembly 102 by withdrawing by partially fastener 210 fromthe aperture 208. When the fastener 210 is withdrawn from the aperture208, the top edge of the fastener 210 pushes downward against theannular extension 206 b, thereby withdrawing the shaft 104 from themotor coupling 122, as indicated by the position of the top end 202 ofthe shaft 104 in configuration 200 a. While the process of withdrawingthe shaft 104 might allow the shaft to fall out of the motor coupling122 under the influence of gravity, the presence of the annularextension 206 b provides additional downward force to ensure that theshaft 104 disengages despite possible friction due to thermal expansionor slight flexion of the shaft 104 (which might otherwise prevent theshaft 104 from disengaging easily).

Importantly, the keys 204 a and 204 b of the shaft 104 remain coupled tothe pinions 106 in both configurations 200 a and 200 b. This couplingenables that the shaft assembly 110 (and particularly the pinions 106)to remain engaged with the rack assembly 140 corresponding to eachpinion 106 and enables the rack assemblies 140 to move freely when theyare pushed or pulled upon while the shaft 104 is disengaged from themotor assembly 102. Notably, even in configuration 200 a, the shaftassembly 110 remains fully assembled. In the event of a motor failure, auser of the sliding support mechanism needs only to loosen the fastener210 to restore (manual) functioning of the mechanism.

In certain embodiments, one or more of the keys 204 a and 204 b areconfigured to prevent each fastener 210 (and thus the shaft 104) frombeing completely removed from the aperture 208 when the shaft assembly110 is fully assembled. In other embodiments, each fastener 210 may beprovided with a visual indicator (such as a colored area, a line, orother marking) indicating how far the fastener 210 (and therefore theshaft 104) may be safely withdrawn.

FIG. 3 presents exploded views of an example of the upper pinionassembly 220, an example of the lower pinion assembly 230, and anexample of the shaft 104. Ancillary components such as screws may beshown, but not labeled. The upper pinion assembly 220 is shown with itscorresponding upper shaft housing 120 and lower shaft housing 130, alongwith its pinion 106, upper bearing 126, and lower bearing 136. The motorcoupling 122 is shown attached to the upper shaft housing 120 belongingto the upper pinion assembly 220.

Similarly, the lower pinion assembly 230 is shown with its correspondingupper shaft housing 120 and lower shaft housing 130, along with itspinion 106, upper bearing 126, and lower bearing 136. Although in thisFigure the shaft housings that belong to the lower pinion assembly 230are labeled identically to those for the upper pinion assembly 220, theystructurally differ as previously discussed. In particular, the lowershaft housing 130 of lower pinion assembly 230 is dimensioned to containthe aperture 208, which is configured to receive the fastener 210, aspreviously described. Also shown are the annular extensions 206 a, and206 b.

Also pictured in FIG. 3 is the shaft 104, with its top end 202 andbottom end 212. The keys 204 a and 204 b are shown on the surface of theshaft 104, and the locations of the annular extensions 206 a and 206 bare indicated (as previously described in reference to the lower pinionassembly 230).

During the operation of the system, or when the supported object isdeployed, the racks 142 and pinions 106 may be subject to forces thatwill tend to cause misalignment leading to poor gear mesh, which in turncan result in structural damage and malfunctions. Accordingly, allelements of the mechanism are judiciously designed and structured toaccommodate realistic amounts of displacement. For instance, each rack142 is made deeper than the teeth of each pinion 106 are long, allowingeach pinion 106 to remain fully engaged even if such pinion is displacedaway from the corresponding rack 142. Similarly, the vertical extent ofthe rack is larger than the vertical extent of the teeth of the pinions106, allowing the shaft 104 and pinions 106 to move up and down withinan acceptable range while the pinions 106 remain fully engaged with eachrack 142.

In further reference to the configuration of the housing of the motorgearbox assembly 102, currently accepted and produced industrially, suchhousing may be substantially cylindrical both at the portion of themotor gearbox assembly 102. Further details of the discussedconstructions are shown in FIG. 4.

FIG. 4 is a cross-sectional view illustrating elements of someembodiments presented above. FIG. 4 depicts a portion of the slidingsupport mechanism 100. This example shows a lower pinion assembly 230engaged with a rack assembly 140. In this example, the shaft assembly110 (represented by only the lower pinion assembly 230) is attached toshaft assembly mount 412 allowing it to be integrated into a largerstructure (not shown). The rack assembly 140 is shown coupled to a frame410 of an object (not shown) to be supported. The object (not shown) isalso partially supported from below by a roller or conveyor 414. Thisexample illustrates an application in which the mechanism 100 may besubject to external forces. For instance if the shaft assembly 110 isrigidly coupled to a larger structure using the shaft assembly mount412, and the frame 410 of object being supported is not perfectly flat,the mechanism 100 will be subject to varying vertical displacements asthe object slides in and out. These and other displacements are managedas described above in connection to FIG. 1B.

Some preferred embodiments include two pairs of mutually parallel rackassemblies 140, each pair disposed on one side of an object. Forexample, the object being supported may be an RV slide-out with one pairof racks on each sidewall. In this example, shaft assemblies would befixed to the sidewalls of the RV (either within recessed compartments orprotruding from the exterior walls). An example application of one suchembodiment is shown in FIG. 5

In the example of FIG. 5, the frame 410 belongs to an RV slide-out 502.The slide-out 502 has a frame 410 on two sides, labeled 410(1) and410(2) for clarity. Each frame 410 is supported by a corresponding shaftassembly 110, labeled 110(1) and 110(2), respectively coupled to a pairof rack assemblies 140. The individual corresponding rack assemblies arelabeled 140(1)(a) and 140(1)(b) on the right side, and 140(2)(a) and140(2)(b) on the left side. Each shaft assembly 110 is configured tocouple to the corresponding shaft assembly support 412, labeled 412(1)and 412(2). Each shaft assembly support 412 is shown as a mountconfigured to couple to the corresponding shaft assembly 110 and furtherconfigured to be installed within the walls of an RV (not shown).

Operational Environment: The Use of Embodiments in RV Slide-Outs

To further explain the benefits provided by embodiments of the presentinvention, aspects of embodiments suited to applications in RVs will benow be discussed in detail. Such embodiments include support mechanismsand motor assemblies used in these support mechanisms, as well asmethods for integrating and employing such support mechanisms and motorassemblies within RVs.

As discussed briefly above, RVs frequently make use of slide-outs toincrease available living space. For instance, a bedroom slide-out mightincrease the size of a bedroom area by extending outward from the wallsof the RV. Typically, these slide outs are supported from below (underthe floor of the module) by a roller or conveyor-type structure. In theconventional slide-outs discussed above, the slide-out will have racksmounted to each of two sides which are perpendicular to the outer wallsof the RV. These racks engage with a shaft coupled to motor which drivesthe slide-out in and out. Because of the dimensions and weight of suchslide-outs, there will be a dedicated motor for each of the twoperpendicular side walls.

It should be understood that these slide-outs may not be entirely rigid.For instance, the floors may bend, flex, and warp over time. Inaddition, uneven distribution of weight within the slide-out module dueto furniture of the presence of people inside them may also causenon-uniform displacement in the floors. Such unevenness will often leadto one side of the slide-out being displaced upward or downward withrespect to the opposite side. In addition, as the slide-out is deployed,it is cantilevered over the ground. Since only the portion of the slidein contact with the walls or floor of the RV is supported, the racks onboth sides will experience a torque which will tend to rotate theslide-out with respect to the racks. In addition, if the racks aredriven by a rotor and shaft, the racks will experience a back-torquethat will tend toward twisting the slideout relative to the walls of theRV. If a slideout support is not properly designed, all these forces canlead displacement and flexure of various components of the supportmechanism leading to poor gear mesh between the racks and the respectiveshafts used to drive the racks. Poor gear mesh can ultimately lead toexcessively worn gear teeth and eventual failure of the mechanism.

Because such mechanisms rely on motors with very high gear reductions(due to need for the motors to fit unobtrusively with the walls of anRV), it can be extremely difficult or impossible to manually deploy orstow and RV slide-out if one or more motor fails. As a result, it isimportant to provide a means of decoupling the racks from the motors toallow the shafts to turn.

With these concerns in mind, deficiencies of related art RV slideoutsupports become evident. An example related art slide-out mechanism usedin thousands of RVs or more every year uses a splined shaft rather thandistinct pinions coupled to a bearing-mounted shaft as disclosed herein.The example related art mechanism does not connect the motor/brakesolidly to the upper pinion housing in order to provide a means forseparating the motor/brake from the pinion gears (the splines) which aremeshed with linear gear racks mounted to the sides of the slide-out.Separating the motor/brake from the splined shaft pinion gear assemblyis required to be able to manually push the slide-out back in for travelshould a drive failure occur.

This example, mechanism of related art replaces the motor/brake threadedholes intended to bolt the drive motor/brake to a drive housing, withfour set screws loosely fitting in holes in the housing. An externalscrew, threaded through the wall channel and into a cooling slot in themotor/brake, keeps the motor engaged with the splined shaft assembly.This attachment design enables removing the external screw and pryingthe motor/brake up manually, disconnecting it from the splined shaftassembly. This enables pushing the slide-out in manually from outsidethe RV.

By contrast, the disclosed embodiments allow for bolting the motorassembly 102 solidly to the upper pinion housing 220 and provides asecondary means for disconnecting the motor from the pinions 106, aspreviously discussed.

An additional advantage is realized by allowing the pinion housings(220, 230) to float up and down with the slide-out since the motor isnot anchored to the outside wall. This is important since up and downmovement of the slide-out occurs when the slide-out (representedschematically by object 410 of FIG. 4), rolling on rollers beneath(represented schematically by rollers 414 in FIG. 4) does not moveperfectly in plane with the pinion housing assembly fastened to theoutside wall (represented schematically by shaft assembly mount 412 inFIG. 4). In embodiments disclosed herein, the pinion housings (such asthe pinion housings 220 and 230 shown in FIG. 2) are floated up and downby surfaces (e.g., upper wear surface 124 and lower wear surface 134) onthe pinion housings (220, 230) that ride against surfaces on each rackassembly 140 to the side of the slide-out. This movement is allowed andguided with proper slide bearing surfaces.

Another advantage of embodiments disclosed herein is the way gear pitchcircle alignment is maintained between the pinions 106 and the racks142. This is accomplished in certain embodiments by providing camfollower type bearings (as bearings 132) in the pinion housings that runinside the U-shaped channel 148 contained in the rack assembly 140.These cam follower type bearings in the pinion housing are fore and aftof each pinion 106 and prevent each pinion from being pushed in or outrelative to the corresponding rack 142.

The loose fit of the pinion housings 220 and 230 with the wall mountingchannel (see 412(1) in FIG. 5) allow in and out and up and down movementas described earlier. In and out movement translates to side to sidemovement of the slide-out. Allowing for this is important since theslide which is rolling on rollers beneath it may be steered left orright as the slide-out is retracted or extended. If the slide-out issteered to press one bearing housing of the bearings 132 into thechannel 148 causing it to bottom out in the channel 148, gear alignmentis still maintained by the bearings 132 in the pinion housing (i.e., 220or 230) pushing against the rack assembly 140 and forcing the slide-outto be pushed away. Similarly, on the opposite side of the slide-out, thebearings 132 on the opposite side pull the pinion housing (220 or 230)out of the channel 148 while still maintaining proper gear mesh.Secondarily, the force of the drive motor acting between the pinions 106and the racks 142 produces a twisting force on the pinion housings (220,230). This twisting is partially reacted against by the housing tryingto turn in the wall channel but is also satisfactorily reacted by havingfore and aft bearings 132 reacting against this twisting force.

Yet another advantage of certain embodiments of the proposed slidingsupport mechanisms is the use of replaceable low friction bearings forthe bearings 126 and 136 in the housings (220, 230) that the shaft 104turns in. The reaction of the gear force is carried in these bearings.Lowering this bearing friction increases the force available to drivethe slide-out.

As mentioned embodiments herein provides a means of disconnecting shaft104 from the motor assembly 102 to allow manual retraction of the slide.The motor assembly 102 is connected to the shaft 104 using a standardfitted coupling (represented as motor coupling 122). The motor shaftextension is round with a flat surface that mates with an internal flatsurface in the coupling and the end of the shaft 104 is machined to ahexagon shape to mate with the internal hex of the coupling (see FIG. 2,for example). To disconnect the motor assembly 102 from the shaft 104the shaft 104 is simply withdrawn from the motor coupling 122. Thecoupling 122 is prevented from disengaging from the motor assembly 102.Drawing the shaft out of the motor coupling 122 causes disengagement ofthe shaft 104 and free movement of the slide-out. The upper and lowerpinions 106 stay engaged with the shaft 104 because the internal keywaysin the pinions 106 (see keys 204 a and 204 b and their positions withinthe pinions 106 in FIG. 2) are long enough to stay engaged when theshaft 104 is pulled out of the motor coupling 122. The end 212 of theshaft 104 (see FIG. 2) opposite the coupling end 202 is extended andmachined for wrench flats to be able move the slide with a wrench whenshaft 104 is disengaged.

It is the very practical use of the sliding support mechanism of theinvention in the RV-environment that raises the question ofunreliability of the industrially-produced motor assemblies 102 andpresents a cause for defining a solution to improving the quality ofsuch motor assemblies. To understand the situation better, the followingdescription first presents the structural characteristics of theconventionally-configured motor assemblies 102. To this end:

FIG. 7A illustrates schematically an embodiment of the motor assembly102, partially exploded to show a motor portion 302 (which contains themotor housing with the motor inside—not shown; and the set of gears orgear train 332) and a rotor portion or assembly 310. The rotor assemblyis additionally detailed in FIGS. 7B and 7C, illustrating, respectively,a cut-out perspective view and a side view of the assembly 310.

Referring now to FIGS. 7A, 7B, and 7C, illustrating a conventionalstructure of the motor assembly, used in related art: the motor gearboxassembly 102 contains a drive motor portion 302 (or, simply, drivemotor, shown concealed in the typically-cylindrical motor housing), aplanetary gearbox 304, and the rotor assembly portion 310.

The rotor assembly portion 310 is structured to include a bearing heldin a respective housing, a rotor or shaft 312, and a faceplate orbearing housing 320, which has an outer face 322 and an inner face 324and through which the rotor/shaft 312 (engaged with the faceplate 320via the bearing) passes. The rotor 312 has a proximal end 312 a and adistal end 312 b. The rotor assembly 310 also includes a gear plate 325,that is coupled to the faceplate or bearing housing 320 (that enclosesthe bearing mechanism shown in FIG. 7B, that carries the threadedmounting holes 336).

The drive motor 302 contains an output motor shaft (not shown) with agear fitted to the end of the shaft and caused to turn with the motoritself. The planetary gearbox 304 contains a set of multi-stageplanetary gear 332 (arranged around a central gear 330), which in atypical embodiment of the motor assembly 102 is coupled to the motor ofthe drive-motor portion 302 and further to the rotor assembly 310 orportion 310, to transfer (in operation of the motor assembly) the motionand associated torque from the motor to the rotor/shaft 312.

As shown, the housing of the drive motor 302 has an outer surface 342,while the housing of the planetary gearbox 304 includes an inner surface344, which may be structured to contain a relief structure. The surface344 is provided with teeth designed to engage or mesh with the outsideof the set of gears 332. The (typically cylindrical) housing of theplanetary gearbox 304 is rigidly joined to the housing of the drivemotor 302 by a fastener (shown as 329A), while the housing of thegearbox 304 is rigidly joined to the bearing housing of the rotorportion 310 with the fastener 329B (and thread or sets of threads 327).

The rotor assembly 310 may also include one or more sets of teeth 328(not shown in FIG. 7A but visible in FIGS. 7B and 7C) disposed on anedge near the inner face 324 of the faceplate 320. The teeth 328 areconfigured such as to engage with the relief structure of the innersurface 344 when the leading end of the rotor assembly, which faces thegears 332 in FIG. 7A, is inserted into and coupled to the housing of thegearbox 304. After this is accomplished, the screw 329B is threadedthrough the corresponding opening in the housing of the gearbox 304 tosecure the portion 310 in its cooperation with the portion 304.

Notably, once the motor assembly 102 has been brought together andassembled (by affixing to one another the drive motor portion 302, thegearbox 304, and the rotor portion 210), the overall motor assembly isfurther cooperated with to be coupled to upper shaft housing 120 (at themotor coupling 122, for example, as shown in FIGS. 1A, 3A) usingfasteners such as screws or bolts and the correspondingly threadedopenings 336 in the face plate 320.

In operation, rotation of the drive motor output gear causes theplanetary gear 332 to turn inside the housing of the gearbox 304. (Here,the stages of the gear in the multi-stage gear set 332 pass on themotion at a reduced speed and increased torque from stage to stage. Forexample, the second stage of planetary gearing contains the samemechanisms as the first stage, except the motor output gear is replacedwith a gear similar to the central gear 330. Subsequent stages duplicatethe second stage up to the output stage. The output stage replaces thegear 330 with the rotor/shaft 312 and transmits the power out throughthe end 312 b.) The intent of this design is that motor 302, the gearhousing 304, and bearing housing 310 are locked together with screws 329A and 329B and the overall assembly 102 is installed with attachmentscrews matching the threads in opening 336, thus creating rotation ofthe shaft 312 at low rpm and high torque.

The applications of the sliding mechanisms, utilizing the motorassembly(ies) 102 and aimed at repeatable repositioning of heavy loadsover hundreds of thousands of times, required that the planetary gearsof the gearbox 304 be appropriately designed to scale up the torquegenerated by the motor of the drive motor portion 302 up to the levelsneeded to rotate the rotor/shaft 312 of the assembly 310. In someembodiments, the torque transfer ratio from the motor to the shaft 312may measure in hundreds. In other words, the ratio of the torque presentat the rotor end 312 to intrinsic torque generated at the input of thegear set by the motor is at least 100, more often 300-500.

The use of such embodiments of motor assemblies in sliding supportmechanisms of the invention leads to a bizarre situation when theconnection between the housing of the gearbox 304 and the faceplate 320of the rotor portion cannot withstand the high-level rotational torquetransferred to the rotor end and “gives in” thereby making the motorassembly non-usable.

Phrased differently, industrial practice convincingly demonstrates thatconventionally-structured motor assemblies 102 (described above and usedin the sliding support mechanisms of the invention) often experiencefailure.

In particular, when such embodiments of the motor assembly 102 are used,the structural features such as the teeth 328 and at least the screw orfastener 329B (designed specifically to prevent the rotor assembly 310from the rotational displacement with respect to the housing of thegearbox 304) s become substantially inadequate for this purpose and are,effectively, stripped away or worn out to the point that the couplingbetween the teeth 328 and the relief of the surface 344 ceases to exist.When such operational condition is reached, the motor assembly 102becomes effectively inutile for extending and retracting the targetslide-out sections and as part of the sliding support mechanism.

That is, the failure of the teeth 328-relief surface 344 and thefastener 329B (which are subject of high torque delivered by themulti-stage planetary gear of the gearbox 304 from the motor of thedrive motor portion 302 to the shaft 312) result in a separation of thehousing of the gearbox 304 from the installed in it bearing housing 322,rendering the assembly 102 unusable. (To enable the reader to visualizethis more clearly, consider rigidly bolting the bearing housing 320 withfasteners in holes 336 to a fixture and forcefully restraining theoutput shaft while powering the drive motor. The torque path goesthrough fasteners 329A and 329B and is reacted at the mounting fasteners336. Since the fastener 329B is much higher stressed than the otherconnections, it fails first. This is the mode of failure practicallyseen in operation of RV slide outs.)

Embodiments of the present invention address this practical problem byproviding a means of mounting the motor assembly at the housing of thegearbox 304 (instead of at the bearing housing 320), thereby eliminatingthe torque connection between the gearbox 304 and the bearing housing320 from which the conventional design of the motor assembly 102suffers. The proposed rotation-prevention andmotor-assembly-to-upper-shaft-housing-attachment arrangement, isstructured to extend outside of the outer surface of the conventionalindustrially-produced housing of the motor assembly (that is, to beseparated from the surface structure 344 by a wall of the motor housing)and to avoid the use of the face plate (or bearing housing) 320 whenattaching the motor assembly 102 to the upper shaft housing 120. Inparticular, embodiments of the present invention are configured tomodify the already-produced, off-the-shelf conventional motor assembly102.

In reference to FIGS. 6A, 6B, and 6C, one non-limiting implementation600 of the motor assembly specifically structured for use with anembodiment of the sliding support mechanism (FIGS. 1A, 3A, 5, forexample) is discussed. A person of skill will immediately appreciatethat operational advantage, provided by the structural differencesbetween the embodiments 600 and 102, ensures that the exploitation ofthe sliding support mechanism that employs the assembly 600 remainsintact for more than 3,100 cycles.

According to the idea of the invention and as shown in FIG. 6A, forexample, the motor portion 302 of the conventional motor assembly 102(and, specifically, the housing of the motor portion 102) is beingjudiciously modified by equipping the motor portion with an outsidestructural component. The chosen structure of the such outsidecomponent, in one implementation, is devised to spatially extend (in aradial direction as viewed from the axis of the motor component 302)beyond the limits of the housing and to provide for such a mechanism ofconnecting the motor portion 302 to the motor coupling 122 (of theembodiment of the sliding support mechanism of the invention, at theupper shaft housing 120, for example) that substitutes theconventionally-used connection between the face plate 325 and the uppershaft housing 120 discussed above.

As shown in the non-limiting example of FIGS. 6A, 6B, 6C, the housing ofthe conventionally-implemented gearbox 304 may be provided orcomplemented with a collar 604 (shown in Figures as a combination of twodistinct components with polygonal perimeters, but more generallyconfigured as a single component with an aperture dimensioned to tightlyfit or accommodate the housing of the gearbox 304 in it). In practice,the conventional off-the-shelf motor assembly 102 is disassembled toseparate the constituent portions 302+304, 310 from one another, andcollar 604 is slided onto (as shown schematically with an arrow 610 inFIG. 6A) and attached to and outside of the housing of the gearbox 304along its perimeter, at or near the edge 614 of the housing facing therotor portion 310 (see FIG. 6B). To ensure the tight fit between thecollar 606 and the housing of gearbox 304, the curvature of the opening618 of the collar 606 is judiciously defined to be substantially matchedto that of the outer surface of the housing in question. Regardless ofwhether the outer diameter of the faceplate or bearing housing 320 issubstantially equal to or exceeds the outer diameter of the housing ofgearbox 304 at this edge 614, the collar 604—once positioned at the edge614—does not interfere with the plate 320. Once the collar 604 isappropriately cooperated with the gearbox 304 (and care is taken to keepthe heads of the fasteners unobstructed), it is irremovably/permanentlyaffixed to the housing of the gearbox by, for example, welding these twocomponent to one another along an edge of the opening 618, to form amodified gearbox 622. (In one alternative, the housing of the gearbox622 may be cast or machined with the collar 604 being an integral partof this housing.) The process of forming the modified motor assembly 600is then completed by affixing the rotor portion 310 to the gear box 622by sliding the leading portion of the portion 310 into the opening ofthe housing of the gearbox 622, meshing the teeth 328 with the surfacerelief 344, and affixing the housing of the gearbox 622 to the faceplate320 with the use of the fastener 329 (in a fashion analogous to that ofaffixing the rotor portion 310 to the gearbox 304 of the embodiment 102,that was discussed above).

Notably, according to one implementation of the idea of the invention,the collar 604 may be equipped with openings 606, configured in afashion similar to that of the openings 336 of the faceplate 320 of theconventionally-complemented motor assembly 102. If this is the case, theopenings 606 are disposed at such radial distance from the axis of thegearbox 622 as to allow for mechanical coupling of the housing of thegearbox portion 622 to the upper shaft housing 120 (at the motorcoupling 122, for example) using fasteners such as screws or boltswhile, at the same time, by-passing the faceplate 320. Notably, as aresult of such mechanical coupling, the faceplate or bearing housing 320of the rotor assembly 310 is operationally decoupled from the amplifiedtorque, transferred from the motor to the rotor/shaft 312 while, at thesame time, maintaining its bearing function. The dimensions andconstruction of the collar 604 and its openings 606 may be chosen basedon the torques the parts must withstand in order to prevent wear andfailure of the coupling between the rotor assembly 310 and the motorhousing 302 for particular motor and gear configurations.

FIG. 6D complements the description of the embodiment of the inventionby depicting the rotor assembly 310 resting in and affixed to themodified gearbox 622 622 and the pinion assembly 112 (counterpositionedwith the motor assembly 600). The motor coupling portion 122 of thepinion assembly 112 is shown with fasteners 626 configured, in the plate630, to reciprocate to and match the openings 606 of the collar 604 andconfigured to be threaded unto the openings 606 in to securely couplethe housing of the motor portion 622 of the motor assembly 600 to theupper shaft assembly 120. A skilled person will unmistakably understandthat, as a result of implementing this mechanical coupling, the jointformed between the rotor portion 310 and the modified gearbox 622substantially is not exposed to the rotational torque produced by themotor of the assembly 600 and scaled up by a factor of at least 100× bythe gears 332 of the gearbox 622. Instead, this torque—as far as itsinfluence on the housing of the embodiment is concerned—is applied tothe combination of the collar 604 and the plate 630, by-passing thecombination of the surface relief 344 of the inner surface of thehousing of the motor portion 622 meshed with the teeth 328 of the rotorportion 310.

It should be understood that, although features described in connectionwith FIGS. 6A-6C are described in the context of example motorassemblies, that some or all of the described features may beimplemented in assemblies which do not require any particular motorassembly shown in the Figures or otherwise described herein.

For the purposes of this disclosure and the appended claims, the use ofthe terms “substantially”, “approximately”, “about” and similar terms inreference to a descriptor of a value, element, property orcharacteristic at hand is intended to emphasize that the value, element,property, or characteristic referred to, while not necessarily beingexactly as stated, would nevertheless be considered, for practicalpurposes, as stated by a person of skill in the art. These terms, asapplied to a specified characteristic or quality descriptor means“mostly”, “mainly”, “considerably”, “by and large”, “essentially”, “togreat or significant extent”, “largely but not necessarily wholly thesame” such as to reasonably denote language of approximation anddescribe the specified characteristic or descriptor so that its scopewould be understood by a person of ordinary skill in the art.

The use of these terms in describing a chosen characteristic or conceptneither implies nor provides any basis for indefiniteness and for addinga numerical limitation to the specified characteristic or descriptor. Asunderstood by a skilled artisan, the practical deviation of the exactvalue or characteristic of such value, element, or property from thatstated falls and may vary within a numerical range defined by anexperimental measurement error that is typical when using a measurementmethod accepted in the art for such purposes. In some specific cases,which are within the scope of the invention, the terms “approximately”and “about”, when used in reference to a numerical value, represent arange of plus or minus 20% with respect to the specified value, morepreferably plus or minus 10%, even more preferably plus or minus 5%,most preferably plus or minus 2% with respect to the specified value.

References made throughout this specification to “one embodiment,” “anembodiment,” “a related embodiment,” or similar language mean that aparticular feature, structure, or characteristic described in connectionwith the referred to “embodiment” is included in at least one embodimentof the present invention. Thus, appearances of these phrases and termsmay, but do not necessarily, refer to the same implementation. It is tobe understood that no portion of disclosure, taken on its own and inpossible connection with a figure, is intended to provide a completedescription of all features of the invention.

It is also to be understood that no single drawing is intended tosupport a complete description of all features of the invention. Inother words, a given drawing is generally descriptive of only some, andgenerally not all, features of the invention. A given drawing and anassociated portion of the disclosure containing a descriptionreferencing such drawing do not, generally, contain all elements of aparticular view or all features that can be presented is this view, forpurposes of simplifying the given drawing and discussion, and to directthe discussion to particular elements that are featured in this drawing.A skilled artisan will recognize that the invention may possibly bepracticed without one or more of the specific features, elements,components, structures, details, or characteristics, or with the use ofother methods, components, materials, and so forth. Therefore, althougha particular detail of an embodiment of the invention may not benecessarily shown in each and every drawing describing such embodiment,the presence of this detail in the drawing may be implied unless thecontext of the description requires otherwise. In other instances, wellknown structures, details, materials, or operations may be not shown ina given drawing or described in detail to avoid obscuring aspects of anembodiment of the invention that are being discussed.

The invention as recited in claims appended to this disclosure isintended to be assessed in light of the disclosure as a whole, includingfeatures disclosed in prior art to which reference is made.

While the invention is described through the above-described exemplaryembodiments, it will be understood by those of ordinary skill in the artthat modifications to, and variations of, the illustrated embodimentsmay be made without departing from the inventive concepts disclosedherein. Disclosed aspects, or portions of these aspects, may be combinedin ways not listed above. Accordingly, the invention should not beviewed as being limited to the disclosed embodiment(s).

What is claimed is:
 1. A sliding support mechanism having a main axis,the mechanism comprising: a first rack and a first pinion, the firstpinion coupled to the first rack, the first rack having a firsttranslational axis; a motor assembly having a drive motor and a gearboxenclosed in a first housing unit, and a rotor portion dimensioned to bepartially inserted in said first housing unit when the motor assembly iscomplete, the rotor portion containing a rotor bearing housing and arotor passing therethrough, wherein the first housing unit includes astructural extension that protrudes radially with respect to the mainaxis and beyond a radial extent of the rotor portion, said structuralextension disposed at an end of the first housing unit that faces therotor portion; a shaft having a first end and a second end, the shaftcoupled to both the rotor and to the first pinion at the first end ofthe shaft; a first bearing configured to receive the shaft and encirclethe shaft at a point between the rotor and the second end of the shaft;an upper housing coupled to the first end of the shaft and directlymechanically attached to said structural extension; and a lower pinionassembly coupled to the second end of the shaft, wherein the lowerpinion assembly includes an aperture dimensioned to receive the secondend of the shaft, wherein the mechanism is configured such that, in afirst state of operation, a fastener is positioned in the aperture suchthat the shaft and rotor are engaged; and in a second state ofoperation, the fastener is withdrawn by at least a fixed distance fromthe aperture, thereby disengaging the first end of the shaft from therotor such that the first rack translates freely along the firsttranslational axis when a force is applied to the support mechanism in adirection parallel to the first translational axis.
 2. The mechanismaccording to claim 1, comprising a set of threads within the aperture,wherein the fastener is threaded.
 3. The mechanism according to claim 1,wherein the rotor bearing housing is not directly affixed to the upperhousing.
 4. The mechanism according to claim 1, further comprising: asecond rack and a second pinion, the second pinion housed in the lowerpinion assembly and coupled to the second rack, the second rack having asecond translational axis parallel to the first translational axis; anda second bearing configured to receive the shaft and encircle the shaftat a point between the second end of the shaft and the first end of theshaft.
 5. The mechanism according to claim 4; wherein, in the secondstate of operation in which the shaft is disengaged from the rotor, themotor assembly is configured to remain coupled to the upper housing. 6.The mechanism according to claim 1, wherein the fastener is threaded andincludes a visual marker along its length; and wherein, when saidfastener is withdrawn from the aperture by less than the fixed distance,the visual marker is hidden within the aperture.
 7. The mechanismaccording to claim 1, wherein the first rack further comprises: an uppersliding surface and a lower sliding surface; a recess configured tosurround the first rack on three sides while leaving teeth of the firstrack exposed; a channel disposed beneath the recess, a roof of thechannel forming a floor of the recess, the channel having an innersurface and an outer surface both extending from the roof of thechannel, a distance between the inner surface and the outer surfacedefining a channel width; and an upper surface forming a roof of therecess; wherein the upper sliding surface includes an upper wearsurface; wherein the mechanism includes a set of at least two rollersand a lower wear surface; wherein the lower wear surface is coupled to,and extends above, the lower sliding surface; and wherein a diameter ofeach of the rollers is smaller than a width of the channel.
 8. Themechanism according to claim 7, wherein the channel is formed of a firstmaterial characterized by a first hardness, and wherein at least one ofthe upper wear surface and the lower wear surface is composed of amaterial characterized by a second hardness that is smaller than thefirst hardness.
 9. The mechanism according to claim 1, wherein at leastone of the following conditions is satisfied: a) said structuralextension is configured as a first flange of the first housing portion,while the upper housing includes a second flange dimensioned such as totransversely protrude from the upper housing with respect to the mainaxis and beyond said radial extent of the rotor portion with respect tothe main axis; b) at least one of the first flange and the second flangehaving a plurality of threaded openings therethrough; and c) the firstand second flanges are removably fastened to one another such that therotor portion is not fastened to the upper housing.
 10. The mechanismaccording to claim 1, wherein said gearbox includes a gear setconfigured to transfer a torque generated at a motor of said assembly tothe rotor with an amplification factor of at least
 100. 11. A slidingsupport mechanism in a recreational vehicle, the mechanism comprising: afirst rack and a first pinion, the first pinion coupled to the firstrack, the first rack having a first translational axis; a second rackand a second pinion coupled to the second rack, the second rack having asecond translational axis parallel to the first translational axis; afirst motor assembly having a first drive motor and a first gearbox,enclosed in a first housing unit, and a first rotor portion dimensionedto be partially inserted in said first housing unit when the first motorassembly is complete, the first rotor portion containing a first rotorbearing housing and a first rotor passing therethrough, wherein thefirst housing unit includes a first structural extension that protrudesradially with respect to the main axis and beyond a radial extent of thefirst rotor portion, said first structural extension disposed at an endof the first housing unit that faces the first rotor portion; a firstshaft having a first end and a second end, the first shaft coupled toboth the rotor and to the first pinion at the first end of the firstshaft; a first bearing configured to receive the first shaft andencircle the first shaft at a point below between the first rotor andthe second end of the first shaft; a second bearing configured toreceive the second end of the first shaft and encircle the first shaftat a point between the first rotor and the second end of the firstshaft; a frame coupled to a recess in the recreational vehicle and tothe first and second racks, the first and second racks coupled to afirst side of the frame; a first housing coupled to the first end of thefirst shaft and to the first motor assembly; and a second housingcoupled to the second end of the first shaft, wherein the second housingincludes a first aperture; wherein the first aperture of the secondhousing is configured to receive the second end of the first shaft;wherein in a first state of operation of the support mechanism a firstfastener is positioned in the aperture such that the first shaft and thefirst rotor are engaged; and wherein in a second state of operation ofthe support mechanism the first fastener is withdrawn by at least afixed distance from the aperture, thereby disengaging the first end ofthe first shaft from the first rotor such that the first and secondracks translate freely along the translational axes when a force isapplied to the mechanism along an auxiliary axis parallel to the firstand second translational axes; the support mechanism further comprisinga set of threads in the first aperture and wherein the first fastener isthreaded.
 12. The mechanism according to claim 11, wherein at least oneof the following conditions is satisfied: a) said first structuralextension is configured as a first flange of the first housing unit,while the first housing includes a first housing flange dimensioned suchas to transversely protrude from the first housing with respect to themain axis and beyond said radial extent of the first rotor portion withrespect to the main axis; b) at least one of the first flange of thefirst housing unit and the first housing flange have a plurality ofthreaded openings therethrough; and c) the first flange of the firsthousing unit and the first housing flange are removably fastened to oneanother such that the first rotor portion is not fastened to the firsthousing.
 13. The mechanism according to claim 11, comprising: third andfourth racks; third and fourth pinions coupled, respectively, to thethird and fourth racks; a second motor assembly, having a second rotor;a second motor assembly having a second drive motor and a secondgearbox, enclosed in a second housing unit, and a second rotor portiondimensioned to be partially inserted in said second housing unit whenthe second motor assembly is complete, the second rotor portioncontaining a second rotor bearing housing and a second rotor passingtherethrough, wherein the second housing unit includes a secondstructural extension that protrudes radially with respect to the mainaxis and beyond a radial extent of the second rotor portion, said secondstructural extension disposed at an end of the second housing unit thatfaces the second rotor portion; a second shaft coupled to the secondrotor and to the third pinion at a first end of the second shaft and tothe fourth pinion at a second end of the second shaft; third and fourthbearings, configured to encircle the second shaft at respective pointsbetween the second rotor and the second end of the second shaft; whereinthe third and fourth racks are coupled to a second side of the frame,the second side of the frame being parallel to the first side of theframe; a third housing coupled to the first end of the second shaft andto the second motor assembly; and a fourth housing coupled to the secondend of the second shaft, wherein the fourth housing includes a secondaperture.
 14. The mechanism according to claim 13, wherein the secondaperture of the fourth housing is configured to receive the second endof the second shaft and the second aperture of the fourth housing iscoupled to a second fastener, wherein the second end of the second shaftis positioned in the second aperture such that the first end of thesecond shaft and the second rotor are engaged while the second fasteneris in a first position, and wherein the first end of the second shaft isdisengaged from the second rotor after the second fastener is withdrawna predetermined distance from the second aperture to a second position,thereby causing the third and fourth racks to translate freely along thefirst and second translational axes when said force is applied to themechanism along said auxiliary axis.
 15. The mechanism according toclaim 14, wherein the first motor assembly and the second motor assemblyare coupled to the first housing and the third housing, respectively;and wherein, during a state in which at least one of the first andsecond shafts is disengaged from a respective one of the first andsecond rotors, the corresponding motor assembly remains coupled to thecorresponding one of the first housing the third housing.
 16. Themechanism according to claim 13, wherein at least one of the followingconditions is satisfied: a) said second structural extension isconfigured as a second flange of the second housing portion, while thesecond housing includes a second housing flange dimensioned such as totransversely protrude from the second housing with respect to the mainaxis and beyond said radial extent of the second rotor portion withrespect to the main axis; b) at least one of the second flange of thesecond housing portion and the second housing flange have a plurality ofthreaded openings therethrough; and c) the second flange of the secondhousing portion and the second housing flange are removably fastened toone another such that the second rotor portion is not fastened to thesecond housing.
 17. A motor assembly having an axis and comprising: adrive motor enclosed in a motor housing; a set of gears housed in agearbox housing that has first and second ends, and coupled to the drivemotor, wherein the gearbox housing affixed to the motor housing at afirst end and having a collar at a second end; and a rotor assemblyhaving a rotor bearing housing, a rotor bearing disposed therein, and arotor shaft passing through the rotor bearing and coupled to said set ofgears, wherein the rotor bearing housing is removably affixed to thegearbox housing at least at an outer periphery thereof, wherein a radialextent of the collar with respect to the axis exceeds a radial extent ofthe bearing housing with respect to the axis.
 18. The motor assemblyaccording to claim 17, wherein at least one of the following conditionsis satisfied: a) the collar is configured to directly affix the gearboxhousing an auxiliary assembly while avoiding a transfer of torque,generated in operation of the motor assembly by the drive motor and theset of gears, to the rotor bearing housing; and b) the rotor bearinghousing includes a teeth structure, the gearbox housing includes arelief structure on an inner surface thereof, said teeth structure isdimensioned to match said relief structure to mesh with the reliefstructure when the rotor bearing housing is removably affixed to thegearbox housing.
 19. The motor assembly according to claim 17, whereinsaid collar carries threaded openings in a portion of the collar that isseparated from the axis by a distance exceeding the radial extent of therotor bearing housing.
 20. The motor assembly according to claim 17,wherein the set of gears is configured to amplify a torque, produced bythe drive motor in operation and transferred to the rotor assembly, by afactor of at least 100.